Overhead ropeway having an automatic clamping device and a lockable load lifter



Au 16, 1966 J. KOLLER. 3,266,639

OVERHEAD ROPEWAY HAVING AN AUTOMATIC CLAMPING DEVICE AND A LOCKABLE LOAD LIFTER Filed Aug. 28, 1963' 5 Sheets-Sheet 2 Aug. 16, 1966 J. KOLLER 3,266,539 OVERHEAD ROPEWAY HAVING AN AUTOMATIC CLAMPING DEVICE AND A LOGKABLE LOAD LIFTER Filed Aug. 28, 1963 5 Sheets-Sheet 3 Aug. .16, 1966 J. KOLLER 3,266,639

TOMATI OVERHEAD ROPEWAY HAVI AN AU 0 CLAMPING DEVICE AND A KABLE LOAD LIFTER Filed Aug. 28, 1965 5 Sheets-Sheet 4 Aug. 16, 1966 J. KOLLER 3,266,639

OVERHEAD ROPEWAY HAVING AN AUTOMATIC CLAMPING DEVICE AND A LOCKABLE LOAD LIFTER Filed Aug. 28, 1963 5 Sheets-Sheet 5 Fig. 10

33 J 97 I 90 3g 97 I 84 l% I 55 I I I F ll/I/ United States Patent O 3,266,639 OVERHEAD ROPEWAY HAVING AN AUTOMATIC CLA'MPING DEVICE AND A LOCKABLE LOAD LIFTER Josef Koller, 1 Endacli, Kufstein, Austria Filed Aug. 28, 1963, Ser. No. 305,158 Claims priority, application Austria, Sept. 8, 1962, 7,176/ 62 13 Claims. (Cl. 212-84) The invention relates to a combined overhead ropeway for conveying loads, comprising a traveling crab equipped with a clamping device and a load lifter interlocked with the crab, in which a reversal of the motion of the traveling crab causes the clamping mechanism to fix the position of the traveling crab on the suspension cable while the release mechanism liberates the load lifter.

The invention is characterized in that the clamping and release device can be actuated after reversal of the motion of the traveling crab by energy accumulated in a reservoir by the motion of the traveling crab along the ropeway; this actuation of the clamping and release device is obtained by forcing gear wheels by means of the reservoir into engagement with a countershaft driven by the rollers of the traveling crab and by providing a hammer shifted by these gear wheels when the motion of the crab is reversed in order to control a changeover valve actuating the blocking and release mechanism, the reservoir being preferably charged by a pump driven by a countershaft.

The invention makes it possible that the switching elements effecting the blocking of the traveling crab and the release of the load lifter can be brought to a preparatory position by means of control elements actuated by the motion of the crab along the ropeway from which the blocking and release can be effected by the switching elements when the motion of the traveling crab is reversed.

Owing to the construction of the combined overhead ropeway according to this invention, during the motion of the traveling crab the switching members are brought into a position, preparing the switching, by means of the respective control elements. Only when the motion of the crab is reversed, do the switching elements effect the blocking or release.

An embodiment of the invention is described with reference to the accompanying drawings. Particularities of the invention and their advantages are explained in detail. The invention 'is, however, not restricted to the embodiment represented. In the drawing:

FIGURE 1 is a perspective side view of the overhead ropeway;

FIGURE 2 shows the overhead ropeway as seen from the opposite side in FIG. 1;

FIGURE 3 is a perspective view in section showing the guide pulley disposed on the traveling crab above the load lifter;

FIGURE 4 shows the portion of FIG. 3 turned through 90 in a position in which the load hook is retracted;

FIGURE 5 is a perspective view of the load lifter in longitudinal section;

FIGURE 6 is a sectional view through the load lifter of FIG. 5;

FIGURE 7 is a perspective view of a switching mechanism;

FIGURE 8 is a view in longitudinal section of a hydraulic reservoir;

FIGURE 9 shows a first preferred embodiment of a clamping mechanism;

FIGURE 10 shows another preferred embodiment of a clamping mechanism; and

lCC

FIGURES 11 and 12 show details of the clamping jaws acting on the suspension cable.

The traveling crab 1 is provided with the usual rollers 2. Through the rollers, by means of a V-belt drive 5 a countershaft 6 is driven when the traveling cr-ab moves, independent-1y of the direction of this motion. The countershaft drives via an adjustable eccentric 12 an oil pump 7. Above the oil pump 7 an oil tank 11 is provided. This oil pump is connected by a feed line 31 containing a control valve 10 with a hydraulic reservoir 8. A further oil line 32 connects reservoir 8 with a changeover valve 20 from which hydraulic lines 33 and 34 lead to respective clamping and release cylinders the operation of which will be discussed in greater detail hereinafter. A further line 35 connects the changeover valve 20 with the oil tank 11 which in turn communicates through a separate line 36 with the control valve 10.

A shaft 30 is disposed above the changeover valve 20 in parallel relation with shaft 6. A lever 14 is supported on shaft 30 and carries a gear wheel 17. Gear wheel 17 is in continuous engagement with a further gear wheel 16, which is rigidly mounted on the shaft 30. A cable line 15 is coupled to and displaced by the cylinder 9 of the reservoir 8 to cause the lever 14 to be swiveled about shaft 30 until the gear wheel 17 engages a gear wheel provided on the countershaft 6. On the shaft 30 a sleeve 28 (FIG. 6) is mounted which can rotate and slide on the shaft. The sleeve is equipped at both ends with jaws. This sleeve is rigidly connected by a lever with a hammer or weight 18. At both sides of the sleeve are mounted clamping jaws which are fixed on the shaft 30. This mechanism is provided above the changeover valve 20. The changeover valve comprises a cylindrical housing in which a valve stem 22 can be displaced against the force of a spring. By means of this stem the oil lines 32, 34 and 35 are connected with each other. The top part of this stern projects beyond the valve housing. On the top face of this valve and concentrically with the valve is a circular guideway 25 on which a circular ring 21 rests and can rotate. On the circular ring 21 two diametrically opposite horn-shaped brackets 19 are supported. The brackets 19 rotate with the ring 21. One horn of each of these brackets is supported on the valve stem 22, the other horn of each of the brackets projecting upwardly from the ring 21 in the swiveling range of the weight 18 to contact the arm of the weight 18 as the ring rotates. A spring 26 acts on the circular ring 21 and maintains the same in an initial position, the function of which will be described hereinafter.

The load lifter comprises essentially a cylindrical tube 23 which is suspended for swivelling movement in the plane of the traveling crab. A hoisting cable 4 carries the load hook 24 and passes along the central axis through the load lifter tube 23. Above the load hook 24 a weight 37 (FIG. 3) is rigidly connected with the cable. In the top part of the tube 23 a helical spring 58 is arranged which is suspended with its upper end in suitable guide bars 59 provided inside the tube. The lower part of this spring moves freely and carries a spring plate 60. Below the weight 37 (with retracted load hook) two diametrically opposite apertures are provided through which two cams 43 and 44 project into the tube. These cams can be displaced against the force of two springs 45 and 46 which urge the cams into the apertures. The earns 43 and 44 are displaced by means of two pegs 47 and 48 which are actuated by a hydraulic cylinder 49. Through a linkage 51 these pegs together with the cylinder 49 arranged between them, can be displaced in a direction away from the tube 23 in a manner as will be described hereinafter. In the locked position of the hook 24, i.e., when the earns 43, 44 project through the apertures in the tube 23 and support weight 37, the pegs 47,

3 48 and the linkage 51 are pressed by the force of the two springs 52 and 53 toward the wall of tube 23.

In the plane through the center of the tube and through the linkage 51, there is provided on the side of the linkage 51 a lever arm 55 which is supported for swiveling movement on the tube 23. This lever arm has an enlarged bottom end 56 which projects through an opening 57 into the tube. The lever arm 55 and the linkage 51 are interconnected by a coupling rod 54.

In the above-mentioned plane, at the opposite side of the tube 23 there is provided a further lever 38, the bottom end of which is formed as a guide rail 39 for a sliding body 40. The sliding body 40 has a nose-shaped boss directed toward the tube 23 and is connected by means of a cable line 27 via guide pulleys with the circular ring 21 mounted on the changeover valve 20. In the tube 23 is formed a slot-shaped axial recess 50 for the nose of the sliding body 40. A spring 61 is positioned between the lever 38 and the tube 23 and due to the force of the spring 61, the lever 38 is urged away from the tube 23. A coupling rod 42 connects via a spring 41 the' lever 38 with the arm 55.

Above the load lifter tube 23, a guide pulley 13 for the hoisting cable 4 is supported in the traveling crab on a shaft 62. On the same shaft, two disks 63 and 64 are located in spaced relation, the disk 64 having a flange or collar which encircles the disk 63. Between the disks is situated a helical spring 65 one end of which is attached to the disk 64, while the other end is fixed to the disk 63. Both disks can be rotated with respect to each other. On the face opposite the guide pulley the disk 63 has a groove into which is engaged a pawl 66 which is loaded by a spring 67, said pawl being attached movably to the guide pulley 13. The other disk 64 is provided with grooves 71 at its circumference (FIG. On the traveling crab 1 a pawl 70 is supported which is pressed by the force of a spring 69 into these grooves 71 (FIG. 2).

The hydraulic reservoir 8 (see FIG. 7) consists of a double-walled cylinder. The inner cylinder 73 guides a piston 75. In the gap between the two cylinder walls a sliding sleeve cylinder 9 is supported which can be displaced outward against the force of the spring 74. This sleeve 9 is connected with the piston 75.

Referring to FIG. 8, the construction of a simple suitable clamping device will be explained. Such clamping device enables the traveling crab 1 to selectively engage cable 3 and thus be locked. The clamping device comprises two jaws 76 and 77 supported on the traveling crab which are urged apart by means of a hydraulic cylinder 79 such that the clamping jaws are clamped against the suspension cable 3. When the cylinder 79 is relieved, the jaws are spaced from the suspension cable by the force of a spring 78 which is interposed between jaws 76 and 77. This construction is suflicient for light overhead ropeways. For heavier types, a construction which proves more suitable is shown in detail in FIG. 9. The clamping device shown therein comprises two tong arms 92 and 93 supported for swivelling movement on the traveling crab 1. Between the top end parts of these two tong arms a hydraulic cylinder 87 is situated. In their lower parts the tong arms 92 and 93 have two rails 82 and 83 provided for the clamping jaws 80 and 81. These rails have at their tops nose-shaped extensions 84 and 85. Above the clamping jaws a toothed rack 86 is arranged at right angles to the cable. Two rams 90 connected with this toothed rack are guided in a rail 94 attached to the traveling crab 1 and are urged upwards by the force of the two springs 91. Between the rail 94 and the toothed rack 86 a further hydraulic cylinder 89 is provided the cross-sectional area of which is only a fraction of that of the cylinder 87. The clamping jaws 80 and 81 are kept separated from the suspension cable by the two springs 88 when the cylinder is hydraulically relieved. The rails 82 and 83 diverge in the direction of the cable winch and the clamping jaws and 81 are constructed in the form of wedges.

Hereafter, the operation of the construction described by this invention will be explained in detail. It is assumed that the load hook carries no load and that the crab 1 travels downward. In this motion of the crab, the countershaft 6 is driven through the V-belt 5 by the roller 2 (FIG. 2). The pump 7 operates from the eccentric 12 and pumps oil from the oil tank 11 through the control valve 10 and the feed line 31 into the hydraulic reservoir 8. The control valve 10 and the changeover valve 2% occupy the positions shown in FIG. 1. The oil pressure in the reservoir 8 acts on the piston 75 and urges the sleeve 9 against the force of the spring 74 towards the right in FIGS. 1 and 7. On its outward movement, the sleeve moves the cable line 15 therewith, thus swiveling the lever 14, together with the gear Wheel 17, toward the countershaft 6 until the gear wheel 17 engages the gear wheel provided on the countershaft 6. When the two toothed wheels are in gear, the gear wheel 17 and hence also the gear wheel 16 mounted rigidly on the shaft 30 are driven by the countershaft. The hammer 18 is in the position shown in FIG. 1 and FIG. 6 and is pressed by one of the brackets 19 under the action of spring 26 against the upper jaw 29. Since the upper jaw rotates clockwise owing to the downward motion of the crab, the jaws undergo ratchet action and freely rotate past each other.

Shortly before the sleeve 9 reaches its extreme position it butts against the valve stem 72 of the valve 10 and shifts this stem toward the right. Thereby the feed line 31 is blocked and the oil pump 7 recycles the oil directly through the line 36 into the oil tank 11. Now, the feed line 31 and the line 32 are under the pressure exerted by the force of the compressed spring 74. The mechanisms will remain in the above-described positions as long as the crab 1 continues its movement. However, if the traveling crab is arrested and if the traveling crab is now arrested and drawn over a short distance in the opposite direction, the sense of rotation of the jaw 29 is reversed and the jaw takesalong the sleeve 28 pressed against it by the bracket 19, and also the hammer. The hammer is lifted and falls down by its own weight at the other side of the shaft 30, striking the second bracket 19. Thereby the bracket is pressed downward and also presses the valve stem 22 downward. Thereby, the lines 32, 33 and 34 are connected with each other and the oil pressurized by the spring 74 passes through the changeover valve 20 into the cylinders 49, and 79 (cylinders 87 and 89 of the embodiment in FIG. 9).

The cylinder 49 actuates the release mechanism of the load lifter by forcing apart the two pegs 47 and 48. Thereby the cams 43 and 44 are retracted from the corresponding apertures in the tube 23 (see FIG. 4) and the weight 37 is free of its support. Owing to the force of the spring 58 the weight 37 is urged downwards out of the tube 23. On its downward course the weight 37 contacts the lever arm 55 and displaces arm 55 away from the tube which takes along in this movement the linkage 51 via the coupling rod 54, thus drawing the pegs 47 and 48 away from the cams 43 and 44. Owing to the force of the springs 45 and 46 these cams spring back into their initial position.

At the same time, oil is admitted into the cylinder 79 which presses the two jaws 76 and 77 against the suspension cable, thus locking the traveling crab to cable 2 (FIG. 8).

In the alternative construction of the clamping mechanism (see FIG. 9), the cylinders 87 and 89 are equally pressurized at the same time and the two jaws 80 and 81 are pressed against the cable. When oil is admitted into the cylinder 89, the toothed rack 86 is pressed down against the force of the two springs 91 and the noses 84 and 85 are engaged in the teeth of the toothed rack 86. If the load hook would be loaded, the traveling crab would be lifted as soon as the load lifter is released. By the rails 82, 83 which are arranged diverging in the direction of the cable winch and are provided as guides for the clamping jaws 80 and 81, these jaws are pressed tightly against the cable due to the wedge effect of the rails (see FIGS. and 11).

Thus, the crab is now blocked, the load lifter is released and may be lowered. When the hook 24 is loaded, the hoisting cable 4 is hauled in. This produces the following effects: the weight 37 enters the tube 23 from below and exerts an outward pressure on the lever arm 55 owing to the conically shaped top part of the weight 37. Thereby, the lever 38 together with the sliding body 40 is urged against the tube by the linkage 42 so that the nose of the sliding body 40 projects through the slots 50 into the tube 23. Thus, the rising weight carries the sliding body upwardly therewith. The spring 58 is compressed. When the bottom side of the weight is situated above the cams 43 and 44, the latter are pressed again into the interior of the tube by the springs 45 and 46. Simultaneously, the enlarged end of the lever arm 55 can again project into the tube, since the spring 52 draws the linkage 51 toward the tube 23 by the coupling rod 54. Since the cylinder 49 is still under pressure, the pegs 47 and 48 are forced apart. The sliding body 40 lifted by the weight 37 actuates the cable line 27, whereby the circular ring 21 of the changeover valve is rotated against the force of the spring 26. Thereby the bracket 19 is withdrawn from below the weight 18, the weight 18 falls further downward and the stem 22 of the valve 20 moves upward. Now, the path is free for the flow of compressed oil from the cylinders 49 and 79 (or the cylinders 87 and 89 in the embodiment of FIG. 9) through the line into the oil tank 11, i.e., these cylinders are relieved and the levers and linkages connected with them return to their initial position. The load lifter is then blocked and the traveling crab is released for further motion. By the action of spring 61 the lever 38 has been urged away from the tube 23 so that the sliding body has been able to fall free from the weight 37 to return to its initial position under the effect of its own weight and the force of the spring 26. Simultaneously with this return the circular ring 21 is rotated counterclockwise whereby the hammer situated at the side of the bracket 19 is pressed against the other jaw. Hence, the initial conditions are reestablished so that after a certain course of the traveling crab and after reversal of its motion the switching operations described above can begin anew to effect the blocking of the crab and the release of the load lifter.

Finally, the function of the helical spring 65 will be briefly explained. When the load lifter is retracted, the disk 63 is rotated via the guide pulley 13 and the pawl 66, whereby the helical spring is wound up. The spring 69 is dimensioned such that it yields only when the helical spring is completely wound up so that only then is the second disk 64 able to join in the rotation; thus, breaking or overwinding of the helical spring is prevented.

If the load lifter is released in the way described above, not only does the weight of weight 37 act on the load hook, but simultaneously also the elastic force of the spring 65 which drives the guide pulley by means of the pawl 66 until the helical spring is completely released. This provides the following advantage: in the constructions known the weight of weight 37 had to be designed such that the relieved load hook was reliably lowered, even when the slack in the cable was very great as a consequence of a small gradient of the cable track. This heavy weight 37 had to be lifted and carried always by the workmen during the loading of the hook. According to the invention, the use of such a heavy weight is avoided in a simple way, since the accumulated force of the spring 58 as well as the helical spring are able to ensure the lowering of the loading hook in spite of slack.

in the cable.

What I claim is: I

1. An overhead ropeway for conveying loads comprising a cable, a traveling crab supported for travel in opposite directions along said cable, said crab including clamping means for engaging the cable to lock the crab therewith, said clamping means having engaged and re leased positions, load lifter means supported from said crab for raising and lowering a load, said load lifter means having retracted and extending positions, and control means for the clamping means and the lifter means to cause the clamping means to assume the engaged position thereof and the load lifter means to move to extended position when the direction of travel of the crab is reversed, said control means comprising power means which is energized by the movement of the traveling crab and switching means for coupling the thus energized power means with both the clamping means and the load lifter means when the direction of travel of the crab is reversed, said control means further comprising a gear wheel driven by the crab as it travels, gear means supported for movementbetween engaged and disengaged positions with respect to the gear wheel, said gear means being driven by the gear wheel when engaged therewith, hammer means controlling said switching means and supported from the gear means for being driven thereby, said power means comprising a reservoir and means coupling said gear wheel with the reservoir to energize the latter as the crab travels.

2. An overhead ropeway as claimed in claim 1, wherein said switching means comprises a changeover valve includinga housing and a stem displaceable on said housing, two swiveling brackets supported for rotation at the end of the stem, the load lifter means comprising a cylindrical tube, a lever pivotally mounted on said tube and having a lower end constituted as a guide rail, a sliding body having a nose-shaped extension supported for movement in said guide rail and a cable connecting said swiveling brackets and said sliding body.

3. An overhead ropeway as claimed in claim 1, wherein said load lifter means comprises a hoisting cable, a rotatable guide pulley for said cable, two rotatable disks arranged in spaced facing relation, a pawl coupling one of said disks with the guide pulley, a spring loaded pawl coupled to the crab and preventing rotation of the other.

disk, one of said disks including a collar encircling the other of the two disks and a helical spring between the two disks, one end of said spring being fixed to the first disk and the other end to the second disk.

4. An overhead ropeway as claimed in claim 1, wherein the reservoir comprises a double-walled cylinder having internal and external walls, a spring-loaded sleeve supported for sliding movement between the cylinder walls, a piston slidably supported within the inner cylinder and engaged with the sleeve to move the same, said control means further comprising a pivotal lever coupled to the piston of the hydraulic reservoir and supporting said gear means for movement between the engaged and disengaged positions thereof, said gear means comprising a first gear which can engage the gear wheel and a second gear in continuous mesh with the first gear and adapted for driving the hammer means.

5. An overhead ropeway as claimed in claim 4, wherein said control means further comprises a rotatable sleeve having jaws at opposite ends and connected to said hammer means and jaw members coupled to said second gear and engageable with the jaws of the sleeve to drive the same and the hammer means therewith.

6. An overhead ropeway as claimed in claim 5, in which said switching means comprises a changeover valve actuated by the hammer means, said changeover valve comprising a cylinder housing, a stern displaceable in said cylinder housing and projecting beyond the housing, two opposite brackets supported for swiveling movement about the axis of the valve, the changeover valve being hydraulically connected with the reservoir and with the clamping means and the load lifter means.

said load lifter means comprises a cylindrical tube supporting said weight and pivotally movable in the direction of travel of the crab, a helical spring in said tube above said weight and having a displaceable lower end which rests upon the weight when the latter is raised.

9. An overhead ropeway as claimed in claim 8, wherein the means for supporting the weight in raised position comprises at least two cams projecting through openings provided in the tube when the weight is raised; said cams being supported for retractable swiveling movement in a plane perpendicular of the tube to be drawn out of their respective openings in the tube, said means for releasing the weight comprising two pegs actuated by said displaceable hydraulic cylinder for retracting the cams from the tube.

10. An overhead ropeway as claimed in claim 9, wherein said pegs and said displaceable cylinder are supported as an assembly, the load lifter means further comprising springs acting on the assembly to urge the same into an initial position.

11. An overhead ropeway as claimed in claim 10, wherein said means .for releasing the weight comprises a pivotally mounted lever on said tube extending lengthwise thereof and having a lower end constituted as a guide rail, a sliding body in said guide rail having a nose-shaped extension, said tube having an axial slot for the nose extension of said sliding body.

12. An overhead ropeway as claimed in claim 11, wherein said load lifter means comprises a further pivotally mounted lever arm on an opposite side of the tube as that of said lever, said arm having a lower end with an enlargement which projects through a corresponding opening provided in the tube into the .interior of the tube, said lever arm being coupled to the said lever opposed thereto.

13. An overhead ropeway as claimed in claim 9, wherein said means for releasing the weight comprises a supporting arm carrying said pegs, a pivotable lever on said tube having a lower end with an enlargement projecting into the interior of the tube, said latter lever being coupled to said supporting arm for common pivotable movement therewith.

References Cited by the Examiner UNITED STATES PATENTS 528,297 10/1894 Jennings 21284 1,069,722 8/1913 Pfouts 212- 1,530,244 3/ 1925 Dickinson 21289 2,429,908 10/ 1947 Allard 21286 2,790,561 4/1957 Wyssen 212-92 3,058,601 10/1962 Wyssen 212--92 X 3,079,008 2/1963 Naud 212-96 X EVON C. BLUNK, Primary Examiner.

SAMUEL F. COLEMAN, HUGO O. SCHULZ,

Examiners.

A. L. LEVINE, A. H. NIELSEN, Assistant Examiners. 

1. AN OVERHEAD ROPEWAY FOR CONVEYING LOADS COMPRISING A CABLE, A TRAVELING CRAB SUPPORTED FOR TRAVEL IN OPPOSITE DIRECTIONS ALONG SAID CABLE, SAID CRAB INCLUDING CLAMPING MEANS FOR ENGAGING THE CABLE TO LOCK THE CRAB THEREWITH, SAID CLAMPING MEANS HAVING ENGAGED AND RELEASED POSITIONS, LOAD LIFTER MEANS SUPPORTED FROM SAID CRAB FOR RAISING AND LOWERING A LOAD, SAID LOAD LIFTER MEANS HAVING RETRACTED AND EXTENDING POSITIONS, AND CONTROL MEANS FOR THE CLAMPING MEANS AND THE LIFTER MEANS TO CAUSE THE CLAMPING MEANS TO ASSUME THE ENGAGED POSITION THEREOF AND THE LOAD LIFTER MEANS TO MOVE THE EXTENDED POSITION WHEN THE DIRECTION OF TRAVEL OF THE CRAB IS REVERSED, SAID CONTROL MEANS COMPRISING POWER MEANS WHICH IS ENERGIZED BY THE MOVEMENT OF THE TRAVELING CRAB AND SWITCHING MEANS FOR COUPLING THE THUS ENERGIZED POWER MEANS WITH BOTH THE CLAMPING MEANS AND THE LOAD LIFTER MEANS WHEN THE DIRECTION OF TRAVEL OF THE CRAB IS REVERSED, 